EP2031272A2 - Amortisseur de vibrations de torsions - Google Patents

Amortisseur de vibrations de torsions Download PDF

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Publication number
EP2031272A2
EP2031272A2 EP08013534A EP08013534A EP2031272A2 EP 2031272 A2 EP2031272 A2 EP 2031272A2 EP 08013534 A EP08013534 A EP 08013534A EP 08013534 A EP08013534 A EP 08013534A EP 2031272 A2 EP2031272 A2 EP 2031272A2
Authority
EP
European Patent Office
Prior art keywords
vibration damper
torsional vibration
sliding shell
energy storage
axial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP08013534A
Other languages
German (de)
English (en)
Other versions
EP2031272A3 (fr
Inventor
Lars Schumann
Michael Bosse
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Publication of EP2031272A2 publication Critical patent/EP2031272A2/fr
Publication of EP2031272A3 publication Critical patent/EP2031272A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/1343—Wound springs characterised by the spring mounting
    • F16F15/13453—Additional guiding means for springs

Definitions

  • the invention relates to a torsional vibration damper with two rotatable about an axis of rotation and against the action of at least one energy storage in the circumferential direction rotatable components, wherein a component by means of an axial approach the at least one energy storage against centrifugal force and a sliding radially between the at least one energy storage the axial Approach is arranged.
  • Torsional vibration damper of this type are for example from the DE 103 10 831 A1 known.
  • a dual mass flywheel torsional vibration damper one or more distributed over the circumference sliding shells are fixedly arranged in their associated components to which energy storage are supported radially under centrifugal force.
  • the task arises to further form the prior art in an advantageous manner.
  • the friction conditions and hysteresis of the energy storage device should be improved.
  • the object is by a torsional vibration damper with two rotatable about a rotation axis and against the action of at least one energy storage circumferentially rotatable relative to each other components, wherein a component by means of an axial approach the at least one energy storage against centrifugal force and supports a sliding radially between the at least one energy storage and the axial projection is arranged, dissolved, wherein the sliding shell is arranged rotatable relative to the axial extension in the circumferential direction.
  • a torsional vibration damper according to the invention may be a damper for damping torsional vibrations, which are caused for example by internal combustion engines.
  • the torsional vibration damper described are therefore particularly suitable for motor vehicles with internal combustion engines and are connected to an input or primary part of the torsional vibration damper with the crankshaft of the internal combustion engine and at an output part to the transmission.
  • a friction clutch On the output or secondary part, a friction clutch may be provided, the clutch disc may be connected to a transmission input shaft.
  • the secondary side or the secondary part may be connected to a torque converter.
  • the torsional vibration damper fulfills the function of a dual-mass flywheel.
  • the two as input and output parts, or as primary and secondary parts against the action of the at least one energy storage rotatable, parallel or serially to the at least one energy storage over the full or partial path of rotation with or without carryover at least a friction device can be switched.
  • the at least one energy store can consist of a plurality of circumferentially distributed spring elements, which can be loaded on pressure and / or train, consist. In this case, several spring groups can be arranged on one or more diameters. Particularly advantageous is the use of so-called bow springs, which can be pre-bent to the insert diameter and therefore are easier to assemble.
  • the energy storage are acted upon rotation of the two components in each case by a stop surface of one and a stop surface of the other component, that is, compressed in compression springs and pulled at tension springs, in which case the springs are suspended in the stop surfaces.
  • At least one sliding shell is provided, to which the at least one energy store can be supported. Because of the high friction, a high hysteresis is observed, in particular during load changes, which is remedied by the fact that the at least one sliding shell can be rotatably received in the receiving component in the circumferential direction.
  • the sliding shell rotates together with the energy store supported on this friction-bearing.
  • the sliding shell can be formed from a plurality of ring segments which distribute over the circumference. In this way, virtually for each energy storage, a segment of a sliding shell, on which this is supported.
  • the individual sliding shells can be arranged directly adjacent to one another in the circumferential direction without play. Also, the sliding shells can be provided with play in the circumferential direction, so that the sliding shells can move independently of each other and without mutually abutment in the circumferential direction.
  • a sliding cup formed in this way can be pulled or punched from flat material and bent into a ring shape.
  • the ring member may be closed, for example, be welded or remain open in elastic design and thus be compensating in the radial direction by widening the diameter.
  • the ring member may be adapted to the outer and / or inner side of the corresponding contours of the support surfaces of the component or the energy storage.
  • the term sliding shell is also used to include such ring parts.
  • the sliding cup is received on an axial projection of a component, which may be the primary or secondary part.
  • a component which may be the primary or secondary part.
  • This axial approach for example by means of metal forming process, such as deep drawing, extrusion or similar processes, formed from the component or as a separate part, for example, as a ring member attached.
  • the component may be shaped so that the axial projection is part of a receiving cage for receiving the energy storage, wherein the axial approach another part may be provided to limit the receiving cage on the opposite side.
  • the rotatable mounting of the sliding shell relative to the axial projection takes place in an advantageously friction-optimized manner by means of a corresponding bearing of the sliding shell and the receiving surface on each other.
  • the sliding shell can be slidably mounted with respect to the axial projection.
  • a lubricant for example oil, grease or a lubricating paste, can be effective between the two parts.
  • the lubricant may be added solid additives such as graphite, molybdenum sulfide, Teflon particles or other substances causing permanent friction reduction.
  • the contact surface of the axial extension and / or its facing surface of the sliding shell may be coated with material having sliding properties, for example, coatings may be provided to form a sliding bearing according to the known Permaglide® principle. It is understood that appropriate measures can be taken to improve the friction properties for the contact surfaces slide rail / energy storage, for example, the sliding shell can be coated on both surfaces. In the same way, the contact surface of the axial extension can be coated. In the case of a lubrication of the sliding shell, it may be particularly advantageous to structure the surface of the sliding shell, for example, pockets for storage to hold on to fat.
  • Structuring can also provide very small cavities, which result, for example, by grinding or other surface treatment methods and generally have a very low surface roughness with an average roughness depth of up to 10-100 ⁇ m.
  • these cavities are also suitable as fat deposits, in particular if plastic is used as the material for the sliding shells and the sliding shells are produced by means of injection molding. In this case, a particularly reproducible surface can be achieved by eroding the injection molding tool used for the parts.
  • a rolling bearing can be provided between the sliding shell and a contact surface of an axial extension of one of the two components which are rotatable relative to one another.
  • a complete rolling bearing of the corresponding design can be introduced radially between the sliding shell and the axial extension and the sliding shell or sliding shells can be accommodated thereon.
  • the slide bearing is at least partially formed of components that already have a suitable form for forming a rolling bearing.
  • the guide rail in the case of an annular design and / or the annular receiving surface on the axial projection can have the receiving profiles for the rolling bodies, so that inner and / or outer rings for the roller bearing are already formed by these parts.
  • the rolling elements are then introduced during assembly of the torsional vibration damper either by means of a Wälz stresses or without such.
  • the rolling elements may be spherical, needle-shaped or barrel-shaped, and novel forms of the rolling elements are encompassed by the invention.
  • Rolling elements are advantageously used whose radial extent is optimized in relation to their load in order to keep the torsional vibration damper with respect to its radial dimensions at advantageously large diameter, on which the energy storage devices are arranged, or to accommodate large energy storage capacities for a given diameter.
  • the axial projection can be configured so that an annular groove is introduced for receiving the rolling bearing.
  • the annular groove can receive an outer ring of a roller bearing in such a way that a lateral wall of the annular groove by means of the axial extension and the opposite wall by means of an additional, connected to the axial neck ring part are formed.
  • a component of the two mutually rotatable components, a molded-on this axial approach and a side attached to the axial neck ring member to form a torus are formed so that housed within the torus, the energy storage and the sliding shell become.
  • an annular groove may be provided on an inner contact surface on the outer circumference, which already results in the manufacture of the parts by means of metal forming processes or is subsequently incorporated, for example by means of a metal-cutting process.
  • FIG. 1 shows a schematically illustrated embodiment of a torsional vibration damper 1 with two against the action of the energy storage 2 rotatable components 3, 4 in section.
  • the torsional vibration damper 1 is driven by a drive unit, not shown, such as internal combustion engine or internal combustion engine in the direction of rotation of the arrow 5.
  • the connection with the drive unit can take place on one of the two components 3, 4, wherein the respective other component 4, 3 is connected to the output side, for example a transmission input shaft.
  • a separating clutch for example a friction clutch, fluid coupling or hydrodynamic torque converter with or without lockup clutch.
  • the energy stores 2 can be activated by means of at least one friction device provided for hysteresis for widening the absorption and / or emission of energy converted by energy stores.
  • the energy storage 2 to the components 3, 4, the radially outer due to the relative movements occurring during the damping processes Contact surface of the component 3 exposed to special wear. It is therefore an annular running in this embodiment executed sliding shell 8, which may also be cured, introduced radially between the energy storage 2 and the inner surface of the component 3.
  • the energy storage 2 by high centrifugal forces - as shown - are retained in at least partially compressed state, so that between the end surfaces 9 and the abutment surfaces 7, or - not shown the stop surfaces 10 - clearance angle arise at a load reversal to a hard Stop the stop surfaces 7 can lead to the end surfaces 9 of the energy storage 2.
  • the sliding shell 8 is rotatable relative to the component 3, for example by means of a sliding or roller bearing mounted, in the illustrated embodiment, the rolling elements shown between the component 3 and the sliding shell 11 11 in the form of needles or balls to a rolling bearing 12, in which directly the component 3, the bearing outer ring and the sliding shell 8 form the bearing inner ring.
  • FIG. 2 shows an embodiment of a torsional vibration damper in the form of a dual mass flywheel 20 in view with a partial detail to illustrate the internal structure.
  • the two mutually rotatable components are formed by a primary part 21 and a secondary part 22, wherein the primary part 21 is connected to the predetermined primary mass guided by the openings 23 screws with the crankshaft and the secondary part 22 forms a receptacle for a friction clutch with the secondary mass, wherein it already forms a pressure plate by means of provided on the secondary mass friction surface 24 and the receptacles 25 for a clutch housing with pressure plate.
  • the pre-bent bow springs 26 are on the primary side of - not shown - indented in the primary part indentations and radially outwardly flared flanges 27 of a fixedly connected to the secondary part 22, for example, riveted flange 31 acted upon.
  • the preferably two, almost over half the circumference extending bow springs 26 are received in a torus-like annular space 28 which is formed from the primary part 21 and an annular flange portion 29.
  • Both parts primary part 21 and flange 29 may be made by means of Blechumformhabilit tool falling and fixed, for example, welded, riveted, shrunk together or connected in a similar manner.
  • annular space 28 is at least to receive an oil or grease filling for lubrication of the mutually moving components located in the annular space 28, a tight connection of primary part 21 and flange part 29 and a dynamic seal 30, for example in the form of a labyrinth seal, a sealing membrane is advantageous.
  • the bow springs 26 are supported radially on the outside by a sliding shell 32 which forms an inner ring for a roller bearing 34 arranged between the inner surface of the radially outer axial projection 33 of the primary part 21 and the bow springs 26.
  • the inner surface 35 as a contact surface for the bow springs 26 may in cross section the radius of the bow springs 26 be aligned.
  • the surface may be designed to accommodate pockets for storing lubricant accordingly.
  • the size of the pockets can encompass a range from a macroscopic impression of individual pockets to the introduction of microscopically fine structures, for example in the micrometer range by erosion.
  • the outer surface 36 may be prepared for receiving rolling elements and their rolling or, in a modification to the in FIG. 2 shown rolling bearing for a sliding contact with the contact surface of the axial projection 33 of the primary part 21.
  • the outer surface 36 coated, greased and structured according to their surface and pretreated.
  • FIG. 4 shows a detail of FIG. 2 with the toroidal annular space 28 forming the primary part 21 with axial projection 33 and the welded thereto flange portion 29, which forms an axial stop 29a, which can simultaneously carry Zündmark isten for the axial projection, wherein at the contact surfaces a weld partially for fastening the parts can be attached continuously to each other or to the tight connection.
  • Another form of sealing of flange 29 and primary 21 may be sealing tapes, a sealing seat or elastomeric seals.
  • the bow springs 26 contained in the annular space 28 are of - not shown - from the flange 31 projecting flanges 27 ( FIG. 2 ).
  • the flange part 29 belonging to the secondary part is sealed against the primary-side flange part 29 by means of a seal 30 designed as a sealing membrane which can simultaneously have frictional properties.
  • the bow springs 26 are based on the inner surface of the axial projection 33 of the primary part 21 under centrifugal force by means of the rolling bearing 34 from rotatable.
  • the inner surface 35 of the annular sliding shell 32 adapted to the cross-sectional radius of the bow springs 26 forms the inner ring of the rolling bearing 34.
  • the outer ring 38 is formed by a separate part, but can also in a further embodiment of the axial projection 33 with the inner surface 37 as a rolling surface are formed for the rolling elements 39, whereby a component can be saved.
  • the axial projection 33 can be hardened at least in the region of the inner surface 37.
  • the rolling bearing 34 is embedded in an advantageous manner in a provided on the outside of the primary part annular groove 40, which is formed in the illustrated embodiment by introduced in the primary part 21 and in the flange 29 cheeks 41, 42.
  • FIG. 5 shows a partial cross section of the in the Figures 2 and 4 illustrated rolling bearing 34 with an inner ring 43 formed from the sliding ring 32 and the outer ring 38 and the rolling elements 39, which are configured in the embodiment shown as needles and a lateral guide, for example, provided in the inner ring 43 annular collars 44 has. It is understood that corresponding guides can also be provided in the outer ring 38.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Mechanical Operated Clutches (AREA)
  • Vibration Prevention Devices (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)
EP08013534A 2007-08-27 2008-07-28 Amortisseur de vibrations de torsions Withdrawn EP2031272A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007040412 2007-08-27

Publications (2)

Publication Number Publication Date
EP2031272A2 true EP2031272A2 (fr) 2009-03-04
EP2031272A3 EP2031272A3 (fr) 2010-07-28

Family

ID=40011365

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08013534A Withdrawn EP2031272A3 (fr) 2007-08-27 2008-07-28 Amortisseur de vibrations de torsions

Country Status (3)

Country Link
EP (1) EP2031272A3 (fr)
CN (1) CN101377224B (fr)
DE (1) DE102008035136A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016192724A1 (fr) * 2015-06-02 2016-12-08 Schaeffler Technologies AG & Co. KG Désaccoupleur à poulie à courroie comportant des coquilles de glissement
FR3057927A1 (fr) * 2016-10-25 2018-04-27 Valeo Embrayages Amortisseur de torsion et vehicule automobile
US11498684B2 (en) * 2018-12-19 2022-11-15 Ami Industries, Inc. Self-stowage assembly for a seat

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8944925B2 (en) 2010-11-19 2015-02-03 Toyota Jidosha Kabushiki Kaisha Vehicular damper device
KR20130129237A (ko) * 2010-12-09 2013-11-27 섀플러 테크놀로지스 아게 운트 코. 카게 벨트 풀리 댐퍼
DE112013004162A5 (de) * 2012-08-24 2015-05-13 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
DE102016214563A1 (de) 2016-08-05 2018-02-08 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer und Reibungskupplung mit ebensolchem
DE102017127063A1 (de) 2016-12-12 2018-06-14 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
DE102017106231A1 (de) * 2017-03-23 2018-09-27 Schaeffler Technologies AG & Co. KG Torsionsdämpfungseinrichtung
DE102019104813B4 (de) * 2019-02-26 2021-01-21 Schaeffler Technologies AG & Co. KG Riemenscheibenentkoppler mit Schmierstofffluss in Vorzugsrichtung
DE102019115752A1 (de) * 2019-06-11 2020-12-17 Schaeffler Technologies AG & Co. KG Riemenscheibenentkoppler mit einer Rotationsachse für einen Riementrieb einer Verbrennungskraftmaschine
DE102019117770B4 (de) * 2019-07-02 2023-10-05 Schaeffler Technologies AG & Co. KG Torsionsschwingungsdämpfer mit Laserstrukturierung sowie Verfahren zur Herstellung des Torsionsschwingungsdämpfers

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10310831A1 (de) 2002-04-10 2003-11-06 Luk Lamellen & Kupplungsbau Antriebsstrang und Verfahren zu dessen Betrieb

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19758942B4 (de) * 1997-08-01 2009-01-29 Zf Sachs Ag Torsionsschwingungsdämpfer
DE19819824B4 (de) * 1998-05-04 2004-11-04 Zf Sachs Ag Torsionsschwingungsdämpfer mit einer Dämpfungseinrichtung
DE10112644A1 (de) * 2001-03-16 2002-09-19 Zf Sachs Ag Schwingungsdämpfungseinrichtung
JP2005504236A (ja) * 2001-09-17 2005-02-10 ルーク　ラメレン　ウント　クツプルングスバウ　ベタイリグングス　コマンディートゲゼルシャフト ねじり振動減衰器
DE102004024739A1 (de) * 2004-05-19 2005-12-15 Zf Friedrichshafen Ag Abstützelement
DE102004057352A1 (de) * 2004-05-19 2005-12-08 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
EP1612386B1 (fr) * 2004-07-02 2012-01-11 Schaeffler Technologies AG & Co. KG Roue motrice pour l'entraînement d'un appareil auxiliaire d'un vehicule
EP1635080A3 (fr) * 2004-09-10 2007-06-20 LuK Lamellen und Kupplungsbau Beteiligungs KG Dispositif pour coupler deux arbres à déport axial
DE102005034338A1 (de) * 2005-07-22 2007-01-25 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
EP1775496B1 (fr) * 2005-10-13 2013-11-06 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations torsionelles
EP1948973A1 (fr) * 2005-11-10 2008-07-30 LuK Lamellen und Kupplungsbau Beteiligungs KG Amortisseur de vibrations de torsion et dispositif convertisseur de couple hydrodynamique pour chaine cinematique d'automobile

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10310831A1 (de) 2002-04-10 2003-11-06 Luk Lamellen & Kupplungsbau Antriebsstrang und Verfahren zu dessen Betrieb

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016192724A1 (fr) * 2015-06-02 2016-12-08 Schaeffler Technologies AG & Co. KG Désaccoupleur à poulie à courroie comportant des coquilles de glissement
FR3057927A1 (fr) * 2016-10-25 2018-04-27 Valeo Embrayages Amortisseur de torsion et vehicule automobile
US11498684B2 (en) * 2018-12-19 2022-11-15 Ami Industries, Inc. Self-stowage assembly for a seat

Also Published As

Publication number Publication date
DE102008035136A1 (de) 2009-03-05
CN101377224A (zh) 2009-03-04
CN101377224B (zh) 2012-08-08
EP2031272A3 (fr) 2010-07-28

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